Milling machine



1945- R. s. CONDON 2,383,910

MILLING MACHINE Filed June 8, 1942 7 Shets -Sheet 1 I N VENTO/E Arron/vars.

Aug. 28, 1945. R. s. CONDON MILLING MACHINE Filed June 8, 1942 7 Sheets-Sheep 2 TTOENEYS.

Aug. 28,1945. R. s. CONDON 2,383,910

MILLING MACHINE Filed June a, 1942 7 Sh eets-Sheet 3 INVENTOB ATTORNEY-S.

Aug. 28, 1945., R. s. CONDON MILLING MACHINE F iled June 8, 1942 7 Sheets-Sheet 5 TABLE REyE/es/Ns CONTROLLER.

SWITCH Aug. 28, 1945. R. s. CONDON. 2,383,910

MILLING MACHINE Filed June 8, 1942 Sheeis-SheetG c 7155- 750 755 755 g I 756 Aug. 2a, 1945. R. s. CONDON 2,383,910

MILLING MACHINE Filed June 8, 1942 '7 Sheets-Sheet 7 v ?aiented 28, 1945 tilt i i T? ,inei

This invention relates to milling machines, and the principal object is to provide a knee and column type horizontal milling machine which is fitted with a heavy swingable vertical head which virtually transforms the machine into a vertical milling machine when the vertical head is swung about its hinge into operating position and bolted or otherwise locked in such position.

Another object of the invention is to provide the machine with a novel knee brace which ties the front or outer portion of the knee to the base casting.

A further object of this invention is to provide the machine with means for obtaining direct reading of the infinitely variable speeds.

A further object of this invention is to provide the machine with a dog controlled automatic longitudinal table cycle accomplished by' both mechanical and electrical means.

A still further object of this invention is to provide the machine with a novel interlock which prevents the engagement of. the table hand crank when the table screw is rapidly rotating under power feed or power rapid traverse.

Other minor objects will be hereinafter set forth.

I will explain the invention with reference to the accompanying drawings which illustrat several practical embodiments thereof, to enable others familiar with the art to adopt and use the same; and will summarize in the claims the essential feature of the invention, the novel features of construction, and novel combinations of parts, for which protection is desired.

In said drawings:

Fig. l is a transverse vertical section through the horizontal milling machine showing knee brace.

Fig. 2 is a front elevation of the vertical milling head showing the hinged mounting.

Fig. 3 is a vertical section through the vertical milling head.

Fig. 4 is a horizontal section through the column of the machine showing the double V-belt selector.

Fig. 5 is a front elevation of the dial and pointer which directly indicate the speed of the spindle.

Fig. 6 is a horizontal section through the speed back gear selector.

Fig, 7 is a developed horizontal section showing the mechanical feed tabledrive.

Fig. 9 is a diagram of the electrical circuit.

Fig. 10 is a vertical section of the dial feedv rate selector.

Fig. 11 is a transverse section through the dial feed rate selector mechanism.

Fig. 12 is a plan view of the alternate speed back selector.

Fig. 13 is a partial transverse vertical section through the horizontal milling machine showing the alternate heavy duty back gears.

Fig. 14 is an enlarged section on the line i l-it, Fig. '7.

Fig. 15 is a perspective view of the safety interlock.

In the drawings, the numeral it designates the column of the milling machine, while it designates the base, 92 the knee, t3 the saddle, and M the table.

The horizontal spindle drive The drive to horizontal spindle 25 in column l6 is powercd by an electric motor 226 (Fig. 1) which is equipped with a stopping brake'tl. A V-belt pulley 2% is keyed to motor shaft .261: and drives a ll-belt it which drives intermediate shaft 35 through spring loaded pulleys 3th and tile (Figs. 1 and 4). Intermediate -shaft bracket 32 is sup ported on pivot 33 by projecting lugs 32a and 32b. The spindle drive continues through V-belt it which engages V-pulleys em and 3th on intermediate shaft 38 and also engages V-pulley 35 on drive sleeve 35 (Fig. 1 Drive sleeve 36 is journaled in hearings in bracket 3i and carries a small drive pinion 36a. Drive bracket 3i is bolted to bracket 38 and is also attached to and supported on column it.

Drive pinion 36a is in constant mesh with gear 39a of cluster gear 39a, 3922, which cluster is keyed to countershaft 39. The driv is completed to spind1e25 through gear 39?) which meshes with gear 25?) since cluster geariiib, 25:: is splined to spindle 25. Cluster gear 25b, 250 can be shifted on spindle 25 to the right (Fig. 1) to bring pinion 390 into mesh with gear 25c, pinion 390 being The belt speed change mechanism The V-belts 2t and 3d are maintained'in tension by spring 3ld which is backed by nut Me and forces thev keyed but slidable V-pulley cone 3 la on shaft 33 inwardly against V-belt 34. This force against belt 34 is transmitted to double cone V-pulley 3 lb which is keyed but slidably mounted on shaft 30, and which presses against V-belt 29,

the V-belt 23 in turn pressing against V-pulley cone 3lc which is pinned to shaft 33. when the V-pulley cones 3Ia, Nb and Mo are lowered by depressing shaft 33, the V-belt 29 assumes a position on its pulley cones 3lb, 3: at a greater radius, and V-belt 34 assumes a position on its V-pulley cones 3Ia, 3th at a shorter radius by the free shift of double cone lib, and thus the speed of the pulley 35 and of. spindle 25 is reduced. The raising of shaft 34 which is journaled in bracket 32 will correspondingly increase the speed of pulley 35 and of spindle 25.

The means for raising and lowering the double V-belt cones 3la, 3th and 3lc consists of a screw 40 (Figs. 1 and 4) journaled in the column 10 at 40c and 40b (Fig. 4) and rotated by hand wheel "0. This threaded screw 40 operates in a nut '4l which is pivoted in 'a yoke 42 on cross pivots 421:. The projection 42a from yoke 42 (Fig. l) is journaled in projections on bracket 32 at 32c and 32d in rotatable and slidable bearings. As

hand wheel 400 is rotated, nut 4| is achusted along The belt speed indicator The indication of the belt speed is shown by pointer 43 on dial plate 44 (Fig. 5). Pointer 43 is rotated by pin 4la engaging a spiral groove 45a in a pointer shaft 45. As the nut 41 is moved by the hand wheel 40c the pin'4la in said nl1t rotates the pointer shaft 45 and thus turns the pointer a corresponding amount. Dial plate 44 is mounted so that it can be adjustably positioned about pointer shaft 45. This is accomplished by. any convenient means such as that shown in Figs 5 using two screws 42a passing through arcuate slots 42b in dial 44 and entering column It. The

' dial can thus be properly-positioned after the final assembly of the machine by obtaining actual readings of one spindle speed and setting the dial plate 44 so that the pointer 43 will indicate thereon the correct speed reading. The adjustment feature of the dial plate 44 is further advantageous in event the .belt 34 wears or stretches and therefore assumes a new position on its cone pulleys 3la and 3). In this event the cone pulley shaft 30 can be lowered by rotating the hand wheel 400. The amount that pointer 43 is moved in order to can be compensated by adjusting dial plate 44 to bring the pointer indication of speed to the correct reading. In event of undue wear or stretch in belts 29 or 34, the motor 25 can be lowered by sliding the motor supporting bolts'in slots Illa: in column It so that belts 34 and 25 can be again ally to maintain the alignment of V-belts 28 and bring belt 34 back to proper operating position brought into their correct operating'positions on pulley cones Ila, 3th and 3 lo. I The above arrangement provides a drive which will transmit high power since the belts 29 and 34 are maintained at high peripheral speed. High torque is obtained through gear train 35a, 39a, direct to the spindle 25 through gears 39b and 25b, or through gears 39c and 250; and thus high torque, for slow spindle speeds, is not created until the drive has progressed to a point immediately adjacent the spindle 25. The gears in the above drive are so chosen that the range of speeds developed by the belts 23 and 34 through each gear train will produce a continuous infinite speed range from minimum to maximum. The

three divisions of this complete range is shown on dial 44 in Fig. 5.

The means for shifting cluster gears 25b, 250

The shifting of cluster gear 25b, 250, is accomplished by means of a yoke bracket 50 (Fig, 6) the yoke'extension 50a: which projects between gears 25b and 250. Yoke bracket 50 is shifted by rod 5| which is movedlaterally by spur gear 52a meshing with rack teeth 5L1 on said rod 5|. Shaft 52 to. which spur gear 52a. is keyed, also carries a hand knob 52b. Locking'pin 520 looks hand knob 52b in position against supportin bracket 53. Spring 53a functions to force 52b in position against supporting bracket53. Spring 53a functions to hold locking pin 520 into engagement with holes in bracket 53 since the pressure of-spring 53a is backed by supportin bracket 53 and acts against sleeve 52d which engages the spur gear 52a.

A spring 50a (Fig. 6) is compressed between two C-shaped collars 5L1: at each end of a reduced portion of shifting rod 5|, as shown. The two collars 511' at each end of this reduced portion are also held in shifter bracket 50 by collar 5lz. Thus rod 5! may be moved in either direction without carrying shifter bracket 50 with it, but in so doing bracket 50 is put under spring pressure to move in said direction. Therefore hand knob'52b can be moved to position the cluster gears 25b and 250 either for clutch engagement with pinion 38x, or gear engagement with cluster gears 39b or 390 by first pullin out the hand knob 52b and turning same to the correct position and allowing spring 53a to bring pin 52a into its desired hole or position. If the gears of the cluster 25b, 250 should strike the faces of the cluster gear 39b, 390, or against the face of the clutch teeth 36a: so that shifter bracket 50 would be unable to directly move, then shifter rod 5| would compress spring 50a and yieldably place shifter bracket 50 under tension, so that when the motor 26 was actuated the shifter 55 would carry the sliding cluster gear 25b, 250, into correct mesh as soon as the gear teeth or clutch teeth were rotated into the correct position to mesh. The knee brace brace 60 which is secured to the forward end of knee .l2 as'at 50b. Knee i2 engages ways Illa (Fig. 4) 'on column I 0. Knee brace 60 therefore serves as an additional supportior the knee I2, 1

and since the knee I2 is already well supported with an extended gibbed slide l2a, the knee on my milling machine is exceptionally well supported. Either'one clamp 60a is used, or more than one may be used in which latter case the ewes-cm W nd' fea h Th Qv t a msi 55 are hound upwardly and outu ardlyg-against their; e SPieCtil/e bores, n 1 3. '1 v "1;;-

: Arbor support v61 i s 3 split horizontally atv 61b and is clamped tooyerarms fi' inby utilizing cla np li'l a which draws the upper half oflarbo r support lil'down against the lower half by the' actionof screw'which engagesscrew threads in the lower halt as shown, The cutters 6 8"are held- Ont-arbor.69 by' the usual seriesof spacing sleevesand a nut as shown. The. one bushing of the; arbor 69 is journaled in the support rehearse; 68 is held inspindle 25 by forcin of the the jtaperegl J Thecooling'system i and ran for tab1e"|4, the coolant flow' through opening": 14 in the table an recteq' into l3k lby thepl'ates shown. f antisthen'returnegi to a I I The; hand land power controls: for the table Thefhandif'andi power"- and? oiitrols for tame-14m t e longitudinal," a erelie'ed.

vertical glirectionsi are shown in'Figs The table l4 rests on" sagld transverseidefie'ca :saddle i I 3' in *myinillingr machine has 8% is kei e" saiasiitiftt siibports' the saddle ts length,*=aiidethe saddl is-formedto create atoi'zhou'seith'e 'riecessaryig'earlngaTherefdreg the a; length which" ives s' 's'uflicient dovetail rsupport' for the table? I 431 This? saddlmhasia Lwidth'fsufllcient lformither' proper; support by -thezkneel 12 :11; Since :these ipractical 5 requirements for 5a: we'll-designed isaddle ipreclude'i-the 'usez ofitapproxlmately these dimensions; as LtOiIength 'andLWidth 0f the sa'ddle, I have made adefinite practical gain inl making zuse of'these necessary dimensio'nsandham-added only sufficient depth to the saddle onzea'ch side of theiknee to form the pockets I3eiwliich house vthe longitudinal table-1 drive. igearsx-i The table longitudinal gearztran'smission definitely reflects the expedient of dividing-"said'transmission and putting a smaller-portion to the right (Fig? 7) so that this smalleriportionplus the electric motor which drivesthe tabIeJtranSmission closely {ap proximates rim weight the. larger portion of .:the gear-drive placed to the left (Fig. 7). :I-Thus the weight and: size .at: the, rightqhalf "of the saddle approximately equals lthezweight t'and slzer'at the left mm: the saddle. I 1 The result isi'a definite mechanical vandjstructural 5 advantage as ziwellms a very pleasing} balanced appearance, as viewed from the front oflthe machined: The longitudinal drive for the i table 14 (Figz 'l iszpowered; by electricmotor-flnd through pinion 10b keyed: on the motor. shafts!!!iandxrmeshing with gear: 1 I b integral:-v;with*fr ear 1 Ha =which is keyed'to 'countershaft :H j ournale'd in bearings at each end-in saddle housing i I 31-- (Figs: :1: and '1) Gear Hav meshes with gearr12acarrying'ia plate lib-riveted to it; Inmate-"12b are housed balls driveniplate 12b will arotate clutchz'sleev 312d;

Clutch s'leeve 12d freely .rotates' soni'bushing 12a which etogethenswithrrsleeve ,l2fiposition it along' sleeve 912 but i permitz its. free.;.rotation: i$ When clutchisleeveg 12g is pushedzto theuright; by; yoke 12h Can-shaft 1211,11; engages the clutch teeth 'of sleeve". 12d a'nd: irotates :or dIiVGSnthtable screw Mb; since:clutchs-sleevetl-zg i'ss'splined to-Bsleev e I2 which in turn is splined to tables'c'r'ew :1 4b. u 'l hus' motors; 1,0115;- driues rtablei screws 1 I .411 'ithroughvithe which is riveted to plate 83b which drives clutch sleeve 83d by means of spring loaded balls similar to those shown at He, in Fig. 14, the balls normally fitting into notches in clutch sleeve 83d in the manner shown in Fig. 14, whereby unless the torque for which the springs are set is exceeded, plate 831) will drive clutch sleeve 83d. A bushing 83c together with sleeve 83/ holds clutch sleeve 83d endwise but allows free rotation thereof. When clutch sleeve 839 is moved to the left (Fig. 7) by yoke 93h on shaft Hilts clutch teeth mesh with clutch teeth on sleeve 83d and thus drives table screw Mb because of the fact that clutch sleeve 839 is splined on sleeve 93 which in turn is splined on shaft Mb.

The power drive from motor a continues from gear 83a to shaft 9! since gear 8lf is in mesh with gear 930. and is keyed to said shaft 8| which drives through'bevel gears 8lg and Sin (Fig. 7) sleeve lily to which gear Blh is keyed. Shaft 96 is slidably keyed to sleeve 8 la and carries clutch 96! which is keyed thereon. When the trip rod lever am is in position shown (Fig. 7)

- trip rod 9! has moved yoke 9) against the action of spring 9lc. A safety clutch assembly consisting of gear Me, which has been drilled to receive spring loaded balls at each end of each hole, is held between the clutch teeth flange of sleeve Sid and collar 9U by nut Mg, and since 9|d and SI) are slightly notched to receive the balls gear 9le will drive sleeve Sid unless the torque, to which the spring pressures to the balls are set, is exceeded. Gear Bic is shown in the drawings positioned so that the clutch teeth of Sid have been withdrawn from the clutch 96 and thus the power would not continue beyond clutch 961'. To effect a power drive from clutch 96! to clutch teeth 91d it is merely necessary to turn trip rod lever 9 I a to the opposite position from that shown in Fig. 7 so that spring 9ic would move yoke 9id whereby gear 91c (and clutch sleeve 9| d) would be moved into mesh with clutch 96f. v

To efiect power drive to the elevating screw i311 (Fig. 1) it is necessary to move trip rod handle 9211 (Fig. '7) on trip rod 92 sothat a fiat 92.1:

on trip rod 92 would allow gear 930. and its clutch teeth to come into mesh with clutch teeth 93! under the urge of spring 920, whereby the drive would continue from gear Me to gear,93a and hence to clutch teeth 93f on shaft 93 (Fig. 7) to which it is keyed; and hence from shaft 93 (Fig.

1) through the keyed bevel gears 931:, 9311 to elevatl ng screw i3d.

To effect a power drive to cross feed screw 900 of saddle i3 it is necessary to move trip rod handle 92a so that the flat on trip rod 92 at 9222.

would permit gear 90c to mesh with clutch teeth 7 90f on screw shaft 900 under the urge of spring 9011. Thus the drive from clutch 96) would continue from gear Ble to 93aand thence to 90c, and then to clutch teeth 90!. Nut i3c which enages shaft 900" is bolted to saddle l3. Gear'93a is mounted on a sleeve 93g' which is flanged and held with screws in housing 94. Such construcone side to slide pinion 951) out of mesh with gear 93a, whereby the hand wheel 95a will not turn during the power drive. When hand drive is desired however, hand wheel 95a is pushed in bringing pinion 95!) into mesh with gear 93a; and thus the hand wheel will turn all three gears 9 id, 93a and 99e. The hand wheel drive can then be i brought to shaft 93 or screw 900 by the action of hand lever 92a, for hand operation, in the same identical manner as when used for power aoperation. Dials 93?; and 90h (Fig. '7) are graduated dials rotatably locked by thumb screws to elevating drive shaft 93 and the saddle cross feed screw 99c, respectively. A similar'dial Mn is mounted on table screw Mb. Bearing 909 is mounted to take the thrust of cross feed screw 990 in both directions.

The three safety clutches or torque release mechanisms in my drive are uniquely placed, and serve a most important role of limiting the torques transmitted at thir points of application in order to prevent breakage and to serve the further purpose of supplying that limit of torque which the gears must be designed to supply. The rapid traverse safety clutch built into plate 12b has slightly spring loaded balls 120 in shallow notches in clutch sleeve 12d because this safety clutch need only be set for light torque to deliver full motor horsepower because the speed of shaft 14b is high. A further advantage of this clutch is that, due to its light torque setting, the balls can ride back and forth in their shallow notches thus releasing the blow' when subject to shock due to clutch engagements actuated by rod i2i or from quick motor reversal loads, thus the impact of engagement of the clutch teeth on sleeve 12d and Hg is greatly lessened. The feed safety clutch of plate 83b, which is generally similar to that of the plate 12b of Fig. 14, has heavily spring-loaded balls however, and sharp angled deep notches in the sleeve 83d, because this clutch must transmit very high torque which is supplied by motor 10a due to the fact that the speed has been greatly reduced through the gear feed transmission. This feed safety clutch together with the'safety clutch built into gear 9ie determines the torquelimit to which the gears in most of the transmissions must be designed to'meet. The safety clutch built into gear 9 le is unique in that this safety clutch is in the power drive to the knee elevating screw l3d (shaft 93) and cross feed screw 900. of the saddle 13, but is not in the hand wheel drive, thus in the event the torque of this clutch is exceeded during power drive the safety clutch will release while in the case of the hand wheel drive the operator is not limited to the setting of the safety 'clutch.

release flats on opposite sides so that it-permits only one clutch pair to be meshed at a time. Thus it has been shown howthe power drive can continue from clutch teeth on 93a to 93f to shaft 93, or can continue from c through sec to.

The safety interlock A safety interlock has been arranged at-i5a (Figs. 7, 8 and 15) on shaft I5 so that the projected lug 151; when swung in place by hand knob [50 will prevent/sleeve 15d from moving to the right (Fig. 7) against the internally mounted gears I and III to sleeve I 00a Journaledin cascompression spring "a: (which spring may be omitted) and which further prevents square pin 'I5e from moving to the right; and thus the clutch teeth on hand crank 15f cannot engage the clutch teeth on collar 159 which is pinned to the table screw Ilb. Thus the hand operation by the hand crank 15] of the table screw is in this way prevented. When hand lever 100 is rotated to bring 15b out of the path of 15d, the hand crank 15) can be moved to the right (Fig. 7) until its clutch teeth mesh with clutch teeth ing HM and supported by the vertical housing g since pin We can then move 15d t the right under spring compression (when the spring is used); and therefore hand crank I5! will en-,

sage and drive the table screw- Mb. Shaft 15 is keyed to pinion 15h (Figs. 8 and 15)which en'- gages rack teeth 16:: in the shaft I6 which may be pulled in or out by hand knob 16a to effect engagement and disengagement of projection 15b on 15a.

The mechanical trip from feed to rapid traverse of the table is accomplished by table trip dogs My (Fig. 15) bolted in the T-slot Ida (Figs. 1 and 15) which depress either plunger I3a or I3b (Figs.

8 and 15) and thus cause pinion Ila together with the shaft 11, to which it is keyed, to rotate. The trip dog that depresses plunger Ila is made so that it will depress same when moving in the chosen feed direction, but it will swing up and not depress this plunger when it goes over the plunger in the return direction. Shaft 17 (Figs. 1, 7 and 15) 12d are caused to mesh. When pointed link 'I'l ii is being rotated it first travels'through th idle space in the slot in rod 121' and proceeds under the point 18a in link I8 before it disengages a set of clutches. The link 18. under the urge of the tension in spring I80 begins to throw the pointed link towardsdzl e opposite clutch set be.- fore the first clutch set is disengaged, and therefore when the movement of the' table has disengaged a set oi clutches, pointed link 18a is in a position to force trip rod 121' to bring the other set of clutches into mesh, thus preventing the mechanism from coming to a dead stop.

In Figs. 8 and 15 cam plate 161: has the cam race 'IBe cut into it so that this cam race is-engaged. by pin 12k in shifter rod Hi, and when rod I6 is inthe position shown in Fig. 8, shifter rod I2i is forced to neutral so that neither clutch is engaged.-- It is this position of rods 18 and 15 in which lug 15b is out of the way of 15d so that hand crank 15 can be engaged by hand as shown in Fig. 17. When hand knob I621 is pulled to the right in Fig. 15, pin 12!: is freed so that shifter rod Hi can engage either set of clutches. 1111 (also Fig. 1) is the hand lever for use in hand operating shaft I1 to select either feed or rapid traverse by the same means used in the power drive. p

The vertical milling head Figs. fend-a illustrate the structural features or the vertical milling head I I I, I I2, which isfastened to column In by means of a hinge] I0 bolted to the side of column I0. The hinge pin I I0a is securely positioned in hinge IIO, so that when it is desired to move the vertical head I II, II2,

into and out of position it is only-necessary to swing it about pin IIIla.-- The drive for spindle I25,is taken from horizontal spindle through V-pulley I05 and from thence. by V-belts to' V-pulley I08, through shaft I01, and through bevel II2. Spindle I2! is slidably keyed in sleeve I00a and is Journaled insleeve I26 which in turn slides in vertical housing II2 under the urge of hand wheel I26a operating screw I281: which engages nut I28c bolted to sleeve I28. Great rigidity for sleeve I26 isobtained by making same relatively large and long and providing a drive on the inside of-it supported as shown with the slot I20d arranged to clear bevel pinion I00. Vertical housing H2 is supported both at II2a and H21) and is supported so that it can rotate in housing II I. Housing H2 is split-for a distance up from its bottom so that screw I I2c can be used for take up for wear, and clamp and screw II can be used to clamp sleeve I20 in housing II2. Screws 2e are used to clamp plates 2! against the groove H29 to effect clamping between housings I II and I I2. Nut I I0!) is rotatable on the threaded lower end of hinge pin I Illa, which pin in turn is secured in hinge IIO bythe screws "Ia, and 7 loosen the V-belts between V-pulleys I05 and I06. Four clamping screws I I Ia are shown used to bolt I housing HI securely against column I0in addition to hinge H0. Screw and nut i266 are used to form an adjustable stop sgt which nut lltc engages when a limit stop for the downward travel of sleeve I20 is desired.

The hand shifting of the table feed change gears The hand direct shifting of the table feed change gears is shown in Fig. 7. Yoke 81a is shown extended to position cluster gear 16b by a yoke disposed between two gears thereof but allowing their free rotation. Similar yokes (not shown) position cluster gear 02b and cluster gear defile, lie. Yoke Ma is pinned to shaft 8'! and is shifted by means of hand lever sly. In the event that the gear teeth of the gear being shifted should hit the face of its mating gear, handle My which is pinned to housing 81b can be moved on into the correct position and be locked by means of pin B11 in oamslots in 81b. Thus when movin handle 079 into desired position the spring are reach its correct position due to striking mating tooth faces, the shaft 01 will force collar 81d which is pinned to the shaft 81 through collar Me,

which is pinned to 819, and force collar 01)? to the right, compressing spring 01h against collar 810 which is stopped at the end of the counterbore in which it rides in 81!). Thus the position of cluster gear Mb can be preselected by hand lever 81g. and if cluster gear Ilb cannot move it will be urged to do so by spring 81h until the gears are so revolved that they can mesh properly.

'Thedial selector The hand shifting may be accomplished by the "dial selector shown in Figs. 10 and 11 which is done by shifting sleeves lglbl, 8lb2or 81b! by mechanical means rather than individually by hand; but the fundamental mounting of springs similar in operation to 01h are used, so that the shifting movement may be accomplished even though cluster gears, similar to Mb, cannot immediately be moved to their correct positions. The mechanical gear shifting device is operated by hand crank 8841 (Fig. which is pinned to shaft 88 which in turn carries gear 88b and a link 880 which carries shifting pin 88d, so that when crank 88a is pushed in against spring 88a to release .pin 88d from housing l3, it can be rotated from positions 1, 2 and 3, shown .in Fig. 11. Sleeve assembly 8ib3 carries a yoke similar to 810 that links into 82b to mesh 82b with 8Id for position 1, with 81b for position 2 and with 8la for position 3. Gear 88!: drives gear 8% so that three turns of handle 88a are required to make one rotation of cam 830 on shaft 89. Cam track 83d is so formed that when handle 88a is rotated to the left (Fig. 11) to assume position 1, 2 and 3 follower pin 89c remains stationary, but when rotated from position 3 to 1 followerpin 88c moves link 89f from its present position and carries 81172 to the left. When hand crank 88a is rotated again from positions 1, 2 and 3 follower pin 89e does not move, but when moved from position 3 to 1 link 83 carries 81172 to its left position. As link 8'Ib2 slides Mb with yoke 810 it successively meshes 14b with Me, Nb and Me. When crank 88a is rotated to position pin 88d successively from -1 to 3 again 83c does not move.

When 88d is now moved from 3 to 1 cam track 8811 carries roller 89e back to the position shown and notch 89!] allows the tension of accumulated over travel .of 8'lbl to pivot link 88h into intimate engagement with 89g and thus link 8312. is forced to pivot with 89m to move 81b! to the cleft. 8'Ibl, through a resilient connection, is yoked to cluster gear He, He and thus pulls ll-e from mesh-with 13c and meshes Hc with'13c. When 88 is again rotated this entire shifting of links 81113 and 81112 are repeated to complete all gear selections. Thus I have shown how the turnin Thus when coil R is energized the table will be driven to the. right by the table motor. Also when coil LT is energized the table will be driven to the left. Spindle motor is operated through the three line contacts labeled on spindle controller as SI, which contacts are closed by solenoid coil S when it is energized because this I coil is actually in position at SI to properly perform this function. Connections are made so that the coolant motor will run when coil 8 is energized providing switches CI, C2 and C3 are connected as shown to the upper set of contacts. If switches Cl, C2 and C3 are connected to the lower set of contacts the coolantmotor will be connected directly to the line and thus receive the necessary incoming power to run. The spindle direction switch is a manually operated direction switch. When all switch links like D3 are positioned by a single manual lever (not shown) and swung to the left the spindle motor will run in one direction when the switch links are swung to the right the spindle motor will run in the opposite direction. When the switch links are positioned vertically as shown,

,-the spindle motor is cut off from power and therefore will not run. The notation 0L labels a safety release placed to protect the motors against overload. There are two 'sets of push buttons used on the milling machine-one at front marked in the diagram Front and the other set marked Rear on diagram. Each has three push buttons Right, Stop. Left, respectively for both sets of push buttons. The double brake contacts marked knee and saddle,are placed in series with the two stop push buttons. The

double brake contact marked JsneeH s depressed ofa hand crank 88a will shift the feed drive gear to positions giving the minimum speed to the positions giving maximum speed. If the hand crank 88a is'turned in the opposite direction the entire operation of the mechanism will be repeated in the reverse order. A dial containing two rows of figures is carried at 891 on dial hub 89k which is keyed to shaft 88 andindicates both the low nine andhigh nine feeds. Dial 89 or any convenient means that-indicates the position of 83h is keyed to pivot pin 83m which is keyed to link 89h so that when link 8971. is shifted by the selector dial, 88 indicates whether the low or high series of feeds are in use. The great convenience of this dial selector makes it attractive over the direct hand shifting means in that it is only necessary to turn crank 88a repeatedly to obtain feed desired as indicated by dial 8!! or c any similar means and dial 897'.

The electric circuit These three lines are regular incoming power lines. The hold-in coil fo -engaging the contacts to operate the motor to propel the table to the right'is shown at R. RI gives the position that this hold-in coil would assume in the control of the table motor. LikewiseLTl shows the position that the hold-in coll LT would assume to operatev the motor in the other direction.

by mechanical trips on the knee and therefore.

stop the knee at a predetermined place or at the limit of its travel. The contact marked "saddle functions in a like manner for the saddle. The contact labeled "LT hold-in" is the standard hold-in contact that is regularly closed when solenoid coil LT is energized and moves bar LTI to close the three contacts for this portion of the table reversing controller. The contact labeled R h'old-in is the standard hold-in contact that is regularly closed when solenoid coll .R. is energized andmoves bar Rl to close the three contacts for this portion of the table reversing controller. The limit switch marked RLS has a double set of contacts oneof which is normallyopen and one is normally closed. Thi limit switch is located at the right end of the saddle and is tripped by table dogs (not own) in T slot Mb in table' I8, when the table is travelling towards the left; The limit switch has a snap action and is loaded by the action of the table dog and trips instantly all the way from th'e normally closed position to close the contacts that are normally open-and opens the contactsthat are normally closed/ Limitswitch-marked us is identical in construction and operation except that it is located at the leftend of saddle and is tripped by table dogs when the table is moving. to the right. That portion of the diagram enclosed by the dotted rectangle and labeled "Automatic control switch" is operated by a single manual handle (not shown) which moves all switch linlm like E3 to the. left when turned towards RL .and brought to a vertical position shown when single manual handle is brought to neutral and pointing to H, and swings all switch links like E3 to the right when single manual handle is turnedtoward the right and brought to RR.

' RR and left is connected to L3, it will be further noted that L2 is carried to the extreme right of the diagram and completes several connections. T2 is brought from the table motor up to a contact on the control switch.

When single manual handle is positioned at H, as explained above, pressing right push button on either front or rear push button station will energize ,coil R as L2 can easily be traced to show that coil R is energized because this coil receives power from both L3 and L2. Energizing coil R closes controller R and starts table motor to drive table to the right.

Table motor will continue to run because R hold-in will be closed and L2 can be easily traced to R through R hold-in. When table motor is started, power from T2 can be traced to. coil 8 and energizes it so that spindle motor will start if spindle direction switch has been manually set for either direction of 'rotation. Coolant motor will run if switches Ci, C2 and C3 are positioned as shown. When the table has continued in its travel until the dog on the left end of the table hits limit switch LLS th'e energizing ollollit to R will stop and thus table motor will stop causing S to be deenergized and therefore coolant is stopped because coil 3 is no lonser en ergized through G3.

When the milling machine is operated as explained above through its automatic cycle the electric controls determine its direction of travel and the synchronizing of the spindle and coolant operation. The feed or rapid traverse rates are determined mechanically by the direction that shifting rod m is shifted (see Figs. 7 and 8). When the machine is run either by hand control of each table movement or by automatic control of a complete table cycle the front .push' button station 94a in Fig. 1 or the rear push button station, both of which are shown in Fig. 9, remains in control so that the milling machine can always be started, reversed orv stopped no I matte where the table is positioned. 1 7

Alternate horizontal spindle-drive The. drive to-the horizontal spindle 25 on column to as shown in Fig; 1 is advantageously simple in operation because the movement of one cluster gear 25b and 260 complete the mesh with their mating gear as well as completing the engagement of the direct drive between the inter nal clutches in 25?) (not shown) and the clutch tured for specially heavy work to gain the advan the spindle motor and coolant motors will stop:

When left push button is pressed coil LTis energized as can beseen by tracing L2 to coil LT when table motor will drive tableto the left, spindle motors and coolant m Table motor will continue to run because LT hold-in will close. When the table dog on right end of table trip RLS the table motor will stop and thus cause spindle motor and coolant motor to stop. It is thus seen that when single manual handle on automatic control switch is positioned at H (meaning hand) the milling ma-' chine *table it will be "right" push button is when left'push button is pressed and will stop when either left or right limit switch is'tripped, or the table can be stopped by pushing stop button in either front or rear push button station and it was shown that whenever the table motor guns the spindle will run and the coolant will OW. i

When single manual the left toward RL above when the ri But when table has the table dogs trips be reversed because energized but in thiscase the spindle motor is stopped because it was being energized along line F3 which is brokenby LLS. Thus, the table will return to the left but spindle and the coolant driven to the right when the machine will .operate as ght push button ispushed. proceeded to the point where LLS the spindle motor will will stop duringv this return travel of the table.

vvWhen single manual handle is turned toward and table will return to the right but spindle and handle is turned to the otors will operate.v

pressed, will go to the left tage of rigidly affixing 225a and 22th to the spindie 2% and avoiding the looseness between the gears and the spindle that would otherwise be unavoidable when these gea s must be slid along the spindle to complete the roper' lntermesh of the gears and clutches. Afurther gain obtained from the alternate drive is that the fly wheel effect of gears 225a and 22th in assisting the cutting teeth in cutter 88 penetratethe surface to be cut and smoothly progressing through the out to give quality finish, is more pronounced when the gears 225a and 22th are definitely red to spindle 225 and not slidably mounted thereon.

The alternate drive to horizontal spindle in volves a, diflerent shifting means because of the fact that both gears I39! and 8390 are moved as' well vas the second part consisting of a clutch sleeve 225d must be moved.

The alternate drive to horizontal spindle as shown in Fig. 13 is powered by belt to. Belt 36 continuesfrom the V-pulleys Ma and Bib exactly identical to. the method previously described and shown in Fig. 1. Pulley 35 again drives sleeve 33 which has pinion 86a cllt integral with it. Pin- R is deenergized and LT is push button i pressed in a similar ion 88a is in constant mesh with gear i390 which is keyed to shaft I39. Gears 43th and "9c are keyed and slidably mounted on shaft its and can be moved into mesh with gear nib-or 2250 orcan be moved out of mesh as shown in Fig.

13. Clutch sleeve 225d is slidably keyed to spindie 22!; Thus spindle 225 can be rotated in slow speed by meshing 22Ic and 1890; in middle speed by meshing 22th and "9b; and in high "speed by meshing 225d withthe clutch teeth on 36a.

Cluster gears lttb'and 139:: are moved by the extended'yolre partially shown at I50 in Fig. 12.

Yoke lid is resiliently mounted on shifter shaft K iii by two U-shaped sliding collars i503: mounted on the reduced portion of shaft i5! and abutting against a compression spring I 50a. Collars I50: also abut against the counterbore in yoke I on one side and against a similar type shoulder produced in any convenient way as shown.

Thus when hand lever I52b rotates rod I52 to which it is pinned, gear I521: is rotated because' it is keyed to I52 and thus rod I51 is moved laterally as gear I52a meshes rack teeth in "SI. If yoke I50 cannot complete the mesh of the gears spring IIla is compressed until the teeth are rotated into mesh. when hand lever I52b is moved to position yoke iioso that gears "9b and I380 aseaelo on the shaft; a plate rotated by the motor; spring pressed balls housed in radial recesses in the plate and engaging notches in the clutch sleeve, thereby providing a safety-clutch whereby the sleeve will be rotated by the-'balls only until the torque for which their springs are set is exceeded.

4. In a machine as set forth in claim 1, each floating clutch element including a clutch sleeve low bell crank to move about its pivot to permit spring I53a to .force shaft I53 to the left and thus carry yoke I530 to the left and thus carry clutch sleeve 225d, which is engaged by yoke I530, to the left to mesh clutch 225d with clutch teeth of pinion 36a. It is therefore shown how hand lever I52b will mesh clutch sleeve 225d with clutch teeth of 35a and also mesh gear. I391) to gear 22% and gear I390 with gear 2250 to complete the drive from'pulley 85 to spindle 225 giving the three speeds. A deep hole as explained above is available to insert pin I520 into it to allow bell crank I53b to complete the mesh of clutch teeth on clutch sleeve 225d. Two shallow holes are used (not shown) to allow pin I52c to enter a short distance to lock hand lever I52b into each of the two positions of this hand lever that mesh I39!) and 2252; or I58'c and 225a. when pin I520 enters these two shallow holes gear I52a moves only slightly under the urge of spring I5la and'bell crank I53b but the slight amount ofnlovement of shaft 1511s not enough to mesh the clutch teeth on clutch sleeve 225d by action of the yoke I530 which is keyed to shaft I53. Thus spring I530 acts to force both the meshing of the clutch teeth on clutch sleeve 225d and also acts to force pin I52c into its locked positions through the madam the bell crank me.

' I claim: a.

1. In a milling machine. a base, a column having a spindle; a vertically movable knee mounted on said column; a transversely movable saddie mountedon said knee and carrying a fixed nut; allongitudinally movable table mounted on said saddle; a feed screw shaft journaled in' said table and engaging the nut; a motor mounted in one end of. the saddle; a clutch member floating on the adjacent end of the shaft and coristant ly driven by said motor for rapid traverse movement of, the table; a second clutch member floating on the opposite end of the 'screw shaft; changespeed gearing mounted in the opposite end-of the saddle and adapted to constantly rotate-the second clutch member for selective feeds of the table; means for driving the change speed gearing from the motor; movable clutch elemer ts splined on the shaft adjacenttheir respective floating clutch elements, and a common actuating member for alternately shifting the movabfeiclutch elements into engagement with 'thei related floating clutch elements.

2. In a machine as set forth in claim 1, said motor and drive for the first floating clutch member being disposed in a depressed, pocket of the saddle below the table at one side of the sada die; and the change speed gearing for the second floating clutch member being disposed in a second depressed pocket of the saddle below the table at the opposite 'side of the saddle, whereby the weights of the divided table drive will be approximately balanced at each side of the saddle.

3. In a machine as set forth in claim 1, each floatin clutch element including a clutch sleeve feedscrew shaft, while the springs'for the balls of the second floating clutch member being heavy and the notches sharp angled for delivering high torque at reduced speeds of the feed screw shaft.

5. In combination, a machine as set forthin claim 1, a hand crank journaled adjacent. the feed screw shaft; a normally disengaged clutch between the crank and shaft; a manually rotatable shaft beside the screw shaft; and 9. lug on said manually rotatable shaft adapted in one positlonto engage the said clutch.

6. In combination, a machine as" set forth in claim 1, a, hand crank journaled adjacent the feed screw shaft; a normally disengaged clutch betweenthe crank and shaft; a manually rotatable shaft beside the. screw shaft; and a lug on said manually rotatable shaft adapted in one position to engage the said clutch; said manually rotatable shaft carrying a pinion; and a manually operable pull rod having rack teeth meshing with .said pinion.

' ber engaging a cam slot in the common actuatref ing member whereby as the crank shaft is rotated in either direction the actuating member will be shifted accordingly to engage either the feed or rapid traverse clutches selectively.

8. In a machineas set forth in claim 1, a pair of spaced plungers mounted in the saddle adjacent one edge of the table; shiftable'trip dogs on the table adapted to actuate the plungers; and a manually rotatable crank shaft underlying the common actuating member and having a member engaging a cam slot in the common actuatcam slot having an idle space; a spring-pressed link having a pointed projection under which the crank passes before shifting the common actuating member to disengage a clutch set, said point- .ed projection throwing the crank towards the opposite clutch set before the first set is disengaged, whereby when the movement of the table has disengaged a set of clutches the springpressed link will he in a position to force the oommonactuating member to engage the other set of clutches while preventing the mechanism from coming to adead stop.

aseaero 13. In a machine as set forth in claim 10, said 9. In combination, a machine as set forth in claim 1, a hand crank journaled adjacent the feed screw shaft; a normally ,disengaged clutch between the crank and shaft; a manually rotatable shaft beside the screw shaft; and a lug on said manually rotatable shaft adapted in one position to engage the said clutch; said manually rotatable shaft carrying a pinion; a manually operable pull rod having rack teeth meshing with said pinion; a cam plate carried by the pull rod and having a cam race; and a pin on the common actuating member, whereby when the pull 'rod is in position to release the lug and engage thehand crank with the feed screw shaft, both sets of clutch elements will be disengaged from the power feed, and whereby when the pull rod is in position to disengage hand crank, the cam race will free the pin so that the common actuating member can engage either set of clutch elements.

10. In a milling machine, a base, a column having a spindle; a vertically movable knee mounted on said column; a transversely movable saddle mounted on said knee and carrying a fixed unit; K

alongitudinally movable table mounted on said saddle; a feed screw shaft journaled in said table and engaging the nut; a motor mounted in one end of the saddle; a clutch member floating on the adjacent end of the shaft and constantly driven by said motor for rapid traverse movement of the table; a second clutch member floating on the opposite end of the screw shaft; change speed gearing mounted in the opposite end of the saddle andadapted to constantly rotate the second clutch member. for selective feeds of the table; means for driving the change speed gearing from the motor; movable clutch elements splined on I the shaft adjacent their respective floating clutch elements, and a common actuating member for alternately shifting the movable clutch elements into engagement with their related floating clutch elements; change speed gearing in the spindle drive; manual control means for shifting the change speed gearing of the spindle drive; separate manual control means for shifting the change speed gearing of the feed shaft drive; and a dial selector for setting the change speed gearing of the feed shaft drive. 1

11. In a machine as set forth in claim 10, said change spe d gearing for the spindle drive and feed shaft drive including intermeshing cluster gears; yokes engaging the respective cluster gears; manually rotatable shafts for operating said yokes; hand knobs on said shafts having pins adapted to engage slots in their supportin ele merits; and yieldable connections between the hand cranks and shafts-for urging the yokes into the preselected positions to which the hand cranks are set, whereby in event the teeth of the cluster gears should initially strike when shifted, the yokes will move said gears into meshing relation whereby the gears will mesh when same have been rotated relatively into. meshing positions.

12. In a machine as set forth in claim 10, said change speed gearing for th feed shaft including intermeshing cluster gears; yokes for operating the respective cluster gears; sliding sleeves operated by the dial selector and carrying said yokes; yieldable connections between the sleeves and yokes for urging the yokes into preselectedpositions to which the sleeves are set, whereby in event the teeth of the cluster gears should iniwhen theg'ears have been rotated relatively into meshing positions.

'dial selector comprising three shifting'rods operating the change speed gears; a normally locked siidable shaft having a hand crank and having an offset pin adapted to engage a slot in one rod when the shaft is shifted; a pinion on said shaft; a gear meshing with said pinion and making one-third of a revolutionfor each revolution of the pinion; a circular plate having-a cam track carried by said gear; a link having a follower engaging said track and operating the second rod; a pivoted link having one end engaging the third rod and its other end overlying the periphery, of the plate; said plate having a notch whereby during one 'arcuate movement of the plate the tension of the accumulated overtravel of the third rod will cause the link to pivot its other end into intimate engagement with the notch and shift the third rod; and said track being so shaped that turning the hand crank through successive rotations will progressively shift the feed shaft drive from minimum gear ratio to maximum with respect to the speed of the motor shaft.

14. In a milling machine, a base, a column having a spindle; a vertically movable knee mounted on said column; a transversely movable saddle mounted on said knee and carrying .a fixed nut; a

longitudinally movable table mounted on said saddle; a feed screw shaft journaled in said table and engaging the nut; a motor mounted in one end of the saddle; a clutch member floating on the adjacent end of the shaft and constantly driven by said motor for rapid traverse movement of the table; a second clutch member floating on the opposite end of the screw shaft; change speed gearing mounted in the opposite end of the saddle and adapted to constantly rotate the second clutch member for selective feeds of the table; means for driving the change speed gearing from the motor; movable clutch elements splined on the shaft adjacent their respective floating clutch elements, a common actuating member for alternately shifting the movable clutch elements into engagement with their related floating clutch elements; a slidable shaft journaled in the knee and extending to the front of the machine and driven by said change speed gearing and carrying a fixed clutch element; a sliding clutch element on said shaft carrying a gear; means for engaging and disengaging the slidable and fixed clutch element; a knee elevating shaft journaled in said knee; a saddle crossfeed screwshaft journaled in said knee; and means for selectively rotating the knee andsaddle shafts from said gear. v

15. In combination with a machine as set forth in claim 14, said sliding clutch element including a sleeve upon which the gear of the sliding clutch rotates; said sleeve having an enlargement beside the gear provided with notches in its adiacent face; said sliding clutch gear having bores registering with said notches; and opposed spring load balls in said bores, thereby providing a safety clutch whereby the gear will be rotated by the balls only .until the torque for which the springs are set have been exceeded.

16. In a machine as set forth in claim'14, said selective rotating means comprising fixed clutch elements on the knee elevating shaft and saddle cross-feed shaft respectively; sliding clutch elements on said knee and saddle shafts; said sliding'clutch elements having intermeshing gears one of which constantly meshes with the gear onthe sliding clutch element of the sliding shaft;

ing clutch elements having intermeshing gears one of which constantly meshes with th gear on the sliding clutch element of the sliding shaft; and means for shifting the sliding clutch elements of the knee and saddle shafts into engagement with their related fixed clutch elements to drive the knee and saddle shafts from the slidin shaft; and a hand crank shaft movably mounted beside the knee elevating shaft and having a gear adapted to mesh with the gear on the sliding clutch element of the knee elevating shaft; and means for normally shifting the movable shaft to disengage said gears, whereby said knee elevating shaft and saddle cross-feed shafts may be manually rotated independently of the power teed.

ROBERT S. CONDON. 

